Transmission mechanism



May 28, 1935. J. NIEDERHAUSER TRANSMISSION MECHANISM" Filed Sept. 1, 1931 4 Shets-Shet l m 365 s xawa may 222 l W a z M; R .Y Ma? AW m m TN W ORQA. .1 0 0 m 1 T z Ks mm m F0 WY 3 a F B m M M 2 w 36 5 5 7 9w 2 5 7 222 2 M 2 2 22 M v j 4 3%? w? 0 @QCQYZ 330 .2 v. 4 M I w; I oum w May 28, 1935.

J. NIEDERHAUS ER v TRANSMISSION MECHANISM Fi'led Sept. 1, 1931 4 Sheets-Sheet 2 J. 0 I 4 4 J 4 2/ 0 .0 0 $00 009 id mx 6C. 90 9 /I/ INVENTOR. J'AAOB N/EDEFf/Al/SER BY 9A. a,

ATTORNEY May 28,.1935. J. NIEDERHAUSER TRANSMISSION MECHANISM Filed se it. 1, 1931 4 Sheets-Sheet 3 74 fmawArb INVENTOR JAKQB N/[DEEHAUSl-"P BY 2&8. M

ATTORNEY May 28, 1935. J. NIEDER HAUSER 2,002,709

TRANSMISSION MECHANISM Filed Sept. 1, 1951 4 Sheets-Sheet 4 ICQ? nn-1mm ATTORNEY Patented May 28, 1935 UNITED STATES PATENT OFFICE TRANSMISSION MECHANISM Jakob Niederhauser, Wettingen, Switzerland, as-

signor of one-half to Richard Suter, Cleveland,

Ohio

Application September 1, 1931, Serial No. 560,575

8 Claims.

in speed of the driven shaft.

One object of my invention is to provide motor vehicles with a transmission mechanism deprived of the heavy and expensive cog wheels and gear shifting device, reducing thereby the weight of the vehicle and affording an easier operation.

Another object of my invention is to secure a transmission mechanism affording a smooth and flexible action similar to the one obtained by fluid transmission but eliminating the costly and impractical packing members necessitated in transmission of that type.

Other objects and advantages more or less auxiliary to the foregoing and the manner in which the various objects are attained, reside in the specific construction and grouping of the elements peculiar to this structure, as will become apparent from a more complete examination of this specification, in the claims of which there are assembled certain combinations of parts and specific constructions indicative of the scope and spirit of the invention.

In the drawings:

Figure 1 is a longitudinal view partly in section illustrating a part of a motor housing and a driven axle housing with the invention incorporated therein.

Figure 2 is a transversal sectional view taken in a plane illustrated by lines 22 in Figure 1.

Figures 3 and 4 are views similar to Figure 2 illustrating parts of the mechanism in different positions.

Figure 5 is a transverse sectional view taken in a plane illustrated by lines 5-5 in Figure 3.

Figure 6 is an enlarged sectional view partly in section illustrating a portion of the rear axle housing assembly.

Figure 7 is a transversal sectional view taken in a plane illustrated by the line 1--1 in Figure 6.

Figure 8 is a longitudinal sectional view taken in a plane illustrated by the line 88 in Figure 7.

Figure 9 is a sectional view taken in a plane illustrated by the line 9-9 in Figure 6 and looking in the direction of the arrows.

Figure 10 is a. developed view of the transmission ratio mechanism.

Figures 11 and 12 are views simliar to Figure 10 illustrating a portion of the transmission ratio mechanism with the partsin different position.

Figure 13 is a view similar to Figure 6 with same parts in different position.

Figure 14 is a sectional transversal view illustrating one form of a braking mechanism possible with my invention.

Figure 15 is a longitudinal view taken in a plane illustrated by line l5-I5 in Figure 14.

Figure 16 is an enlarged sectional view illustrating the position of the balls within the conduit.

Figure 17 is an enlarged view showing the different position of the hand operated lever.

Referring now to the drawings in which like symbols designate corresponding parts throughout the several views, there is shown a housing l0 having a shaft ll rotatably mounted therein. This shaft may be connected to a motor by any suitable means. The shaft ll being coupled to a motor will hereafter be denoted as driving shaft or primary unit. Mounted upon the driving shaft ll, there is a gear I2 formed with a plurality of selectively designed teeth l3, engageable with the pressure bodies or balls I. The housing [0 is manufactured to provide an internal semi-circular wall I5, producing with the bottom of the teeth l3, a canal I6 of a diameter somewhat larger than the diameter of the balls l4. Disposed in axial alignment through the housing l0, there are two passages l9 and 20 located adjacent to the ends l1 and I8 of the canal l6. Disposed concentrically with the passages l9 and. 20, and adjacent to the ends thereof, the housing In is formed with two external screw threaded portions 2| and 2|. Intermediate the passages l9 and 20, there is a connecting passage 22. Intersecting said last mentioned passages, there are two cylindrical members or governors 23 and 24 rotatably mounted within the housing It), and having extending shanks 25 fitted to receive the meshing gears 26 and 21. The governors 23 and 24 are formed with cylindrical passages 28 having their opening disposed at right angles from each other. The housing I0 is provided with two other conduits 2B and 30, which are in communication with the governors 23 and 24. The external wall of these conduits are'terminated by a screw threaded portion 3| and 3|.

Therotation of the gear 26 and 21 may be effected in any suitable manner as for instance by the means of a gear segment 32 rotatably mounted upon a stationary shaft 33, and operable by a hand lever 34. Connecting the primary unit II to the rear axle 35, which will hereafter be denoted as driven or secondary unit, there is a system of hollow conduit 36, filled with pressure bodies or balls I4, circulating therein at the will of the operator as will hereafter be explained. The system of conduits is provided with ball reservoirs 38, connected thereto in a manner similar to the one illustrated in Fig. 16. These reservoirs are terminated by a screw threaded portion 39, adapted to receive a screw threaded cap 40, against which there is seated one end of a compression spring M which has its other end engaged over the last ball in the reservoir, the purpose of which will be explained later. The different conduits or tubings of the system can be secured to the primary and secondary units by any suitable means, as for instance a screw threaded coupling 42.

Secured to the casing 35, there are two tubular housings 43 having therewithin the two wheel shafts or driven shafts 44 and 45, which are terminated by a splined portion 46. Mounted upon the shaft 44, there is a wheel 41 provided with a bushing liner 48, and having a tubular hub 49, which is rotatably mounted Within a roller bearing 58, secured to the tubular housing by a screw 52. The wheel 41 is provided with a plurality of radially extending portions or earns 53, the purpose of which will be explained later.

Mounted upon the shaft 45, there is a wheel 54 formed with a bushing liner 55, and provided with a screw threaded hub 56 having a cylindrical portion 51 rotatably mounted within a roller bearing 58 which is secured to the tubular housing 43 by the screws 59. The wheel 54 is integrally secured to the wheel 41 by a plurality of bolts 60, and is formed with a longitudinally extending drum 6I. Intermediate the hub 56 and drum 6|, the wheel 54 is formed for engagement with one end of a compression spring 62 disposed therein with its other end engaging a screw threaded nut 63 operatively mounted upon the hub 56, and provided with a radially extending flange 64 shaped with circumferentially disposed protuberances or teeth 65. The wheels 41 and 54 are adapted to receive a pressed fitted stem 66,

supporting the diflerential gear 61, which is capable of engagement with-the bevel gears 68 and 69. These gears are formed with a bore of a configuration similar to the end of the shafts 44 and 45, and engaged therein against any relative rotation.

Movably mounted upon the drum 6|, there is a tubular member or gear 10, formed with circumferentially disposed cavities 1I. The depth of these cavities is somewhat less than half' the diameter'cf the present "bodies vor "balls I4. Intermediate'iof each d cavities, there is provided a grelatively' wall constituting a tooth 12. 'I'h'efgear 19 has provided upon one of its annular walls. apgroupof denticulations 13, forming a-pluralityjof notches 14. These notches are identical inijdepthl and have their bottom surface 15 in parallel vertical arrangement, with their connecting surfaces1'16 formed with a portion of an inclinedplane,whichextends toward the center axis of the gear. "Each group has its first and last notch 11 and 18 provided with an enlarged bottom surface connected to each other by an inclined wall 19. The other of the annular wall of the-gear 10, is formed with a plurality of equally spaced protrusions 0r teeth 86, engageable with the protuberances or teeth 65.

The housing 35 is provided with screw threaded connections BI and BI extending in opposite direction fitted to receive the end of theconduit system 36, and being provided internally therebetween, with an enlarged groove 82 formed with an integral side wall 83 and rotatable side wall 84, formed by the ball bearing ring 85. The groove 62 is of somewhat greater depth than half the diameter of the balls I4 and is shaped with a curved internal wall 86, parallel to the circumferential wall of the gear 10, and forming with the bottom of the cavities 1I an enlarged canal 81. The gear 10 is of smaller outside diameter than the machined end walls 88 of the canal 81, thus allowing the rotation of the former into the latter.

A braking system of any suitable design can be inserted within the conduit system as illustrated in Figs. 14 and 15 in which 89 is a housing to which clamped, by the bolts 90, a cover 9| provided with a screw threaded bore -92 which is adapted to receive the screw threaded end portion or stud 93 of a hand omrable. lever 94. Longitudinally disposed between the housing 89 and its cover 9I, there is a rectangular bore 95 being connected to the adjacent ends of the conduit 36 through the orifices 96. The bore 95 is shaped in a manner suitable to receive .a brake block 91, engageable with the end of the stud 93, and is provided with a longitudinally disposed semi-circular groove 98. A groove 99 similar to the groove 98 is also provided in the housing 89 intermediate the orifices 96, forming thereby, to-

gether with the groove 98, a conduit similar to In the operation of the mechanism, assuming the shaft I I is being driven by any suitable power, as for instance a gasoline engine, with the coupling mechanism connecting one to the other or with any suitable clutch in the engaging position, and assuming also the lever 34 in the B position, as illustrated by dot and dash lines in Fig. 1'1, the circulation governors 23 and 24 will be positioned as illustrated in Fig. 4. The gear I2 being rotated with the shaft I I in a counter clockwise direction and having its teeth I3 engaging the pressure bodies or balls I4, will set them in motion through the governor 24, canal 22, governor 23 andback to the gear I2. It will obviously be understood that in this position of the governors 23 and 24 the balls I4 are not circulating within the conduit 36 and therefore the rear axle or wheel shafts 44 and 45 do not rotate.

Therefore, the vehicle will be in a neutral position, the engine running without imparting mo-:

- gear I2, by the motor shaft I I, will be transmitted to the balls I4, indulging thereby a circulation of the balls within the conduits 36, the balls being ejected from the connection 2 I to the conduit 99, junction I 0 I, and entering the housing 35 through the connection 8|. Within the housing 35, the balls will be forced into engagement with the gear 10, and impelling a peripheral pressure upon the teeth 12 will obviously propel the gear 10 in a clock-wise direction. Following their regular course or flow, the ballswill again be ejected from the housing 35 through the connections BI, and be returned to their initial place or gear I2 by wayof the conduit 36, junction I82 and conduit 2 I The rotation of the gear 10 is transmitted to the nut 64 through the equally spaced teeth engaging the nuts teeth 64, thus resulting in an axial displacement of the nut 63 toward the left, due to its rotation upon the thread 56 of the momentarily stationary wheel 54. In this axial displacement the spring 62 will be submitted to a greater compression, thus increasing the frictional resistance between the threads 56 and 63 sufiiciently to overcome the frictional resistance ortorque of the rear wheel shafts 44 and 45, affording consequently the rotation of the wheel 54 and 41, and finally the forward motion of the vehicle through the medium of the difierential mechanism and shafts 44 and 45.

It will obviously be understood that the gear l2 of the primary unit and the gear 16 of the secondary unit, are rigidly and forcibly connected to each other by means of the balls or pressure bodies l4, traveling within the conduits. In addition to the advantage of applying a pressure and motive transmission within the conduits between the primary and secondary units, the present invention possesses the outstanding feature of being capable to produce a great range of power transmission ratio. The gear l2 of the primary unit and the gear 10 of the secondary unit are of such a diameter as to produce a minimum transmission ratio suitable for high speed rotation with a minimum torque resistance applied to the rear axle of driven wheel. Assuming now that a greater transmission ratio is necessary as would be required to first set the vehicle in motion from a standstill position, the

' pressure bodies I will circulate within the mechanism as explained previously. However, with the gear 10 in the extreme rightward position, the conduit 82 is limited between the left side wall 1Ia of the cavities 1| and the rotatably but non-longitudinally movable side walls 84 of the ball bearing 85. With the gear 16 in its extreme rightward position, the conduit 82, or the width of the cavities H is of such a size as to maintain the balls l4 one behind the other within the cavities 1|, thus affording a relative rotation of the gear 10 with respect to the cams 53. The gear 10 being rotated by the balls l4, exerting a force normal to the teeth 12, will cause the consequential rotation of the nut 64, by the respective engagement of the teeth 80 and 65. The nut 64 rotated upon the stationary bushing 51, will be displaced axially or toward the left, thus increasing the compression of a spring 62, and also increasing the frictional engagement between the threads 56 and 63. During the relative rotation of the gear 16 in respect to the earns 53, the denticulations 13 will be placed opposite the cams 53, and since the balls [4 also exert an axial force normal upon the side wall 1la of the cavities 1|, the gear 10 will be moved leftwidth of the cavities or conduit 82.

wardly, thus assuring the engagement of the denticulations 13 with the cams 53 as illustrated in Fig. 11. This leftward movement of the gear 16 will efiect the consequential leftward displacement of the side walls 1Ia, thus increasing the The width of the cavities 82 may thus be increased until a plurality of balls come in contact with the teeth 12, or until the denticulations 13 slide over the cams 53 sufficiently to finally permit the engagement of the last land 18 with the cams 53 as illustrated in Fig. 10, thus limiting the leftward axial displacement of the gear 10. The actuating areas of the walls 1Ib, are proportional to the longitudinal displacement of the gear 16, and with this gear in its extreme leftward position as illustrated in Fig. 10, the actuating area of the walls 16 is at its maximum. The circumferential force applied on the teeth- J2, or the rotary power imparted to the gear 16 is directly proportional to the actuating areas 1Ib, thus with these areas at their maximum, the rotary power of the gear 16 will also be at its maximum for a predetermined speed of the driving unit or gear I2.

Attention is directed to the fact that the transmission ratio is directly dependent upon the torque resistance of the wheel shafts 44 and 45. If a great torque resistance is applied to these shafts, it will result in a greater compression of the spring 62 to increase the frictional resistance between the thread 56 and 63, thus allowing a large or maximum axial displacement of the gear 10. It will be observed that, if a smaller torque is applied to the shafts 44 and 45, a smaller frictional resistance between the threads 56 and 63 will be necessary, thus requiring a smaller compression of the spring 61. As explained previously, the compression of the spring 61 is obtained during the relative rotation of the gear 10 and the consequential rotation of the nut 64 with respect to the wheel 51, wheel 41, or cams 53. During this relative rotation of the gear 10, imparted thereto by the balls acting against the teeth 12 and also normal to the side wall 1|a, the gear 10 will be moved leftwardly as explained previously with the denticulations 13 maintained in abutting relation with the cams 53. The leftward longitudinal displacement of the gear 16 will continue as long as there is a relative rotation of that gear with respect to the wheel 51, wheel 41, and cams 53, i. e. as long as the compression of the spring 62 is not suflicient to create enough frictional resistance between the threads 56 and 63 to overcome the torque applied to the shafts 44 and 45. With the longitudinal displacement of the gear 10, it is now understood that the areas of the walls 1 lb are also increased, thus augmenting the rotary power of the gear 10. The longitudinal displacement of the gear or the sliding of the notches 14 upon the cams 53 will be terminated when the spring 62 is sufficiently compressed, thus overcoming the torque applied to the shafts 44 and 45. When this occurs, the denticulations 13 may be positioned and engaged with the cams 53 as illustrated in Fig. 11. After the vehicle is set in motion and is maintained therein with an increasing speed depending upon the accelerated Opening of the power motor fuel supply, the torque resistance applied to the shafts 44 and 45 will diminish requiring thereby a smaller frictional resistance between the nut 63 and the screw threaded hub 56, i. e. a smaller compression of the spring 62. The wheel 54, and consequently the wheel 41 together with the cam 53 will actually be rotated faster than the nut 64 and gear 10, thus affording a step by step engagement of the cam 53 with the denticulation 13 by sliding over the inclined wall 16 of the notches 14, resulting thereby in an axial displacement of the gear 10 toward the right and decreasing therefore the cross sectional area of the conduit 82 or reducing the actuating area. of the walls 1lb with a consequential reduction of the transmission ratio. When the vehicle has finally acquired a normal speed or when a. normal torque resistance is applied to the shafts 44 and 45, the cam 53 willbe positioned for engagement with the land "11 (see Fig. 12) reducing to a minimum the actuating areas of the walls HI} and thereby reducing the transmission ratio to a minimum. I

When driving the vehicle on a decline of the road or down hill, the operator will purposely shut off or reduce the fuel supply to the engine thus reducing the rotative speed of the shaft M, gear l2, and consequently slow the circulation of the balls 3'! within the conduit system; The previously injected circumferential force to the gear teeth H or against the cavity walls 1 lb will have the tendency now to force the balls 31 out through the connection 8| imparting therefore an opposite circumferential force against the cavity walls He and consequently an axial force against the walls I I a and 84 tending to move the gear Ill in a direction toward the left. The nut 63, however, moved by the circumferential force previously'applied thereon by the gear ID, will maintain, together with the wheel 54, wheel 41 and consequently the cam 53, its nominal rotative speed creating thereby a. relative rotation between the gear 10 and the cam 53. The width D of the land 78 being equal or larger than the distance E between the gear and nut projections and 65, the gear 10 will be allowed to move leftwardly when the cams 53 come in alignment or opposite the land 18 affording therefore a greater cross sectional area of the conduit H and increasing thereby the transmission ratio as previously explained. The self inserting high transmission ratio acts as an automatic braking device for the motor. The circumferential speed imparted by momentum to the shafts 44 and 45 will be checked by the circumferential force applied against the cavities llc.

Should it be desired to set the vehicle in a rearward motion, the lever 34 may be moved in the /"C position as illustrated in Fig. 17, rotating thereby through the medium of the segment 32 the governors 23 and 24 in a position illustrated in Figs. 3 and 5.

. The halls l4 being forced through the conduits by the gear l2 will be ejected from the connection 3| into the conduit 36, connection 8| into the housing 35, where they will engage with the gear ID in a manner similar to the one previously described, but imparting an opposite rotation to the gear 10, inducing therefore a rearward movement to the vehicle through the shafts 54 and 55. Continuing their course or flow, the balls 31 will again be returned to their.

initial place or gear i2 through the connection 8|, conduit 36' and connection 3! (Fig. 1).

All conduits and passages are completely filled with pressure bodies or balls l4. To assure compact packing of the conduits, one or several reservoirs 38 are disposed within the conduit circuit, each one of the reservoirs being filled with surplus balls M which. are held under pressure exerted by the springs 4i; consequently such pressure compensates for any existing play or gaps within the conduits, as well as affording a certain elasticity therein.

The braking mechanism disclosed in Fig. 14 and Fig. 15 can be operated at the will of the driver by pulling upon the lever 94 thus imparting pressure upon the balls M through the me dium of the screw threaded stem 93 and block 9'1. The pressure upon several balls will be sufficient to increase any possible circulation of the balls within the conduits system thus maintaining the vehicle in any desired location.

While I have in this application specifically described one form which the invention may assume in practice, it will be understood that this form of the same is shown for purpose of illustration and that the invention may be modified and embodied in various other forms without departingirom its spirit or the scope of the appended claims.

I claim:

1. In a power transmission mechanism, a primary and secondary unit, a gear rotatable within said primary unit engageable with a plurality of spheroidal bodies and capable of imparting thereto a force afiording the circulation of said bodies from said primary unit to said secondary unit, guides or conduits for said bodies, a second gear within said secondary unit adapted to receive said bodies, said second gear being rotatable and axially movable by the forces imparted thereto by said pressure bodies, and means within said secondary unit capable of varying the transmission ratio between said units, said means comprising a load receiving mechanism associated with said second gear and actuable upon variations of load applied thereto for causing the axial movement of said second gear and the consequential variation of said transmission ratio.

2. A transmission mechanism comprising in combination a primary unit having a mounted shaft and a gear, a secondary unit containing a driven gear engageable with a nut, a threaded wheel and a driven shaft, the energy and motion of said driven gear being transmitted to said driven shaft by reason of the frictional resistance of said nut upon said threaded wheel, means for varying said resistance comprising a spring intermediate said wheel and nut, means for axially shifting said driven gear comprising a denticulation upon said gear engageable with a cam, and further means allowing a relative rotation of said driven gear and nut afiording thereby new engagement of said denticulation upon said cam, a system of conduits filled with pressure bodies having actuated surfaces, passages within said units for said bodies, and means for increasing or decreasing the cross sectional area of said passages by the shifting of said driven gear, varying thereby the ratio transmission of said energy and motion.

3. In a transmission mechanism, a primary unit being connected to a secondary unit by a system of conduits filled with bodies having arcuated surfaces for transmitting the energy and motion from one of said units to the other, a braking mechanism within said system comprising means for restricting said conduits preventing thereby said transmission.

4. In a transmission mechanism a primary and secondary unit, a system of conduits connecting said units to each other, a plurality of balls circulating within said conduits to transmit energy and motion from one of said units to the other and a braking mechanism comprising means for preventing the circulation of said balls within said conduits.

5. In a transmission mechanism, a primary and secondary unit connected to each other by a system of conduits filled with bodies having arcuated surfaces for transmitting energy and motion from one of said units to the other, a reservoir connection with said conduits having some of said bodies in storage therein, and pressure means within said reservoir tending to forcibly eject said bodies into said conduits.

6. A transmission mechanism comprising a primary unit including a driving member, a secondary unit comprising a driven member engageable with a nut, a screw threaded wheel upon which said nut is capable of relative rotation, means for transmitting energy and motion from said driving member to said driven member and transmitting the same to said screw threaded wheel by reason of the frictional resistance of said nut, thereon, and means for varying said vfrictional resistance.

'7. A transmission mechanism comprising a primary unit including a driving member, a secondary unit comprising a driven member engageable with a nut, a screw threaded wheel upon which said nut is capable of relative rotation, a load carrying shaft drivably connected with said wheel, means for transmitting energy and motion from said driving member to said driven member and transmitting the same to said screw threaded wheel by reason of the frictional resistance of said nut thereon and to said shaft, and means responsive to a variation of the load applied to said shaft for varying said frictional resistance.

8. A transmission mechanism comprising a primary unit including a driving member, a secondary unit comprising a driven member engageable with a driving element, a driven element capable of frictional interlocking engagement with said driving element, a load carrying shaft drivably connected with said driven element, means for transmitting energy and motion from said driving member to said driven member and transmitting the same to said driven element and to said shaft by reason of the frictional resistance of the engagement of the former with said driving element, and means responsive to a variation of the load applied to said shaft for varying said frictional resistance.

J AKOB NIEDERHAUSER. 

